JP5817908B2 - Control device - Google Patents

Description

  The present invention relates to a control device that controls a vehicle drive device in which a rotating electrical machine and a speed change mechanism are provided in order from the internal combustion engine side in a power transmission path connecting an internal combustion engine and wheels.

  As a control device that controls the vehicle drive device as described above, a device described in Japanese Patent Application Laid-Open No. 2004-316831 (Patent Document 1) is already known. Hereinafter, in the description of the background art section, the description in Patent Document 1 is quoted in []. During the speed change operation, this control device rotates according to the combination of the change direction of the gear ratio (upshift or downshift) and the operating state of the internal combustion engine (when the engine is turned on or when the engine is turned off). Control is performed so that the electric motor [motor / generator 2] adds or absorbs torque. For example, during a downshift when the engine is powered off, the torque of the rotating electrical machine transmitted to the input side rotating member [transmission input shaft 5] of the transmission mechanism [stepped automatic transmission 3] is increased to increase the input side Control for increasing the rotational speed of the rotating member is executed. As a result, it is possible to execute shift control with good responsiveness while reducing shift shock.

  However, in the control device of Patent Document 1, the main body for performing the shift assist by increasing the rotation speed of the input side rotation member during the shift control for downshifting is limited to the rotating electrical machine. Therefore, depending on the situation where the rotating electrical machine is placed, there is a possibility that sufficient torque that is necessary cannot be output. As a result, the target control cannot be properly executed, and there is a possibility that the shift shock cannot be sufficiently reduced.

JP 2004-316831 A

  Therefore, it is desired to realize a control device that can execute an appropriate downshift with excellent responsiveness even in a situation where the torque of the rotating electrical machine is insufficient.

  The power transmission path connecting the internal combustion engine and the wheels according to the present invention is provided with a rotating electrical machine and a transmission mechanism in order from the side of the internal combustion engine, and the engagement state of the shift engagement device provided in the transmission mechanism The control device that controls the vehicle drive device that is configured so that the speed change mechanism can change the speed ratio by controlling the speed ratio is that the speed change mechanism is changed during the downshift when the speed change ratio is changed. A shift assist control unit for performing shift assist control for increasing the rotation speed of the input-side rotating member by increasing the torque of the rotating electrical machine transmitted to the input-side rotating member of the mechanism, and a predetermined target rotation speed A possibility determination unit that determines whether or not the rotating electrical machine can output the required input torque for increasing the rotation speed of the input side rotation member according to the rate of change, and a shift mode. A mode selection unit that selectively selects one shift mode and a second shift mode in which at least one of the downshift start condition and the processing content is different from the first shift mode; When it is determined that the required input torque cannot be output, in the shift assist control, the shortage with respect to the required input torque is transmitted by the shift engagement device and the output torque of the internal combustion engine according to the shift mode. And a torque compensation unit that compensates using at least one of the torques.

  According to this characteristic configuration, when at least the rotating electrical machine can output the necessary input torque, the rotation speed of the input side rotation member can be increased according to the target rotation speed change rate by the shift assist control. Therefore, shift control with excellent responsiveness can be executed. Further, even when the rotating electric machine cannot output the required input torque, at least one of the internal combustion engine and the shift engagement device can compensate for the shortage with respect to the required input torque. At this time, the main body for compensating for the shortage with respect to the necessary input torque is not determined uniformly but variably determined according to the speed change mode. That is, the torque that compensates for the shortage with respect to the required input torque is variably determined according to the shift mode from the output torque of the internal combustion engine and the transmission torque by the shift engagement device. Therefore, the shortage with respect to the required input torque can be appropriately compensated according to the control characteristics of the first shift mode and the second shift mode in which at least one of the downshift start condition and the processing content is different. Therefore, even in a situation where the torque of the rotating electrical machine is insufficient, it is possible to realize a control device that can execute an appropriate downshift with excellent responsiveness.

  Here, the first speed change mode is the automatic speed change mode and the second speed change mode is the manual speed change mode, or the time required for the control for the downshift is the second speed change mode. A mode shorter than the first mode or a mode in which the acceleration response at the time of downshift is higher than that of the first shift mode, and the torque compensation unit takes the shortage into engagement for the shift when the first shift mode is selected. It is preferable to compensate by using the transmission torque by the device, and to compensate the shortage by using at least the output torque of the internal combustion engine when the second shift mode is selected.

  In the above configuration, when the second speed change mode is realized, quick execution of the speed change control and good driving sensation tend to be prioritized over the fuel consumption during vehicle travel, compared to when the first speed change mode is realized. Therefore, when the second speed change mode is selected, the output torque of the internal combustion engine is used to compensate for the shortage with respect to the required input torque, thereby enabling speedy execution of speed change control in a short time while suppressing the occurrence of speed change shock. can do. On the other hand, when selecting the first speed change mode, it is possible to perform a downshift with excellent responsiveness while suppressing a decrease in fuel consumption by compensating for the shortage of the required input torque using the transmission torque from the gear shift engagement device. It can be.

  The possibility determination unit further determines whether the rotating electric machine and the internal combustion engine can output the necessary input torque in cooperation with each other, and the torque compensation unit includes the second speed change mode. If it is determined that the required input torque cannot be output even if the rotating electrical machine and the internal combustion engine cooperate with each other, the transmission torque by the shift engagement device is further used to reduce the shortage. It is preferable to compensate.

  According to this configuration, when the second speed change mode is selected, a deficiency with respect to the necessary input torque is further compensated by further using the transmission torque by the gear shift engagement device under the above-described specific conditions, so that the rotating electrical machine, the internal combustion engine, In addition, the rotation speed of the input side rotation member can be increased by the cooperation of the shift engagement device. Therefore, even when the rotary electric machine and the internal combustion engine cooperate, even when the necessary input torque cannot be output, it is possible to execute downshift with excellent responsiveness.

  Further, the possibility determination unit determines whether or not the rotating electrical machine can output a lower limit input torque for increasing the rotation speed of the input side rotation member according to a predetermined lower limit rotation speed change rate. Further, the torque compensation unit determines the torque transmitted by the shift engagement device on the condition that the rotating electrical machine is determined to be unable to output the lower limit input torque when the first shift mode is selected. It is preferable that the shortage is compensated by using.

  When the shifting engagement device compensates for the shortage with respect to the required input torque, the torque transmitted to the wheels may fluctuate. In view of this point, according to the above-described configuration, only when the rotating electrical machine cannot output the lower limit input torque, the shortage with respect to the necessary input torque is compensated by using the transmission torque by the gearshift engagement device. The opportunity that the torque transmitted to the wheels fluctuates can be minimized. On the other hand, when the rotating electrical machine can output the lower limit input torque, the rotation speed of the input side rotation member can be increased according to the lower limit rotation speed change rate by the shift assist control at the lower limit input torque. Therefore, it is possible to execute shift control with relatively excellent responsiveness while suppressing torque fluctuation.

  Further, the rotational speed of the input side rotating member determined according to the vehicle speed and the gear ratio is set as the synchronous rotational speed, and the lower limit rotational speed change rate is the difference between the synchronous rotational speed before and after the change of the speed ratio, and the change of the speed ratio. It is preferable that the heat generation amount of the shift engagement device slipped at the time is set based on an upper limit shift time determined so as to be equal to or less than a predetermined allowable heat generation amount.

  According to this configuration, the heat generation amount of the gearshift engagement device can be suppressed to an allowable heat generation amount or less while enabling shift control with relatively excellent responsiveness to be executed. Therefore, it is possible to suppress the thermal deterioration of the shift engagement device. Alternatively, it is possible to suppress an increase in the manufacturing cost of the drive device to be controlled by reducing the necessity of increasing the heat resistance of the gearshift engagement device or providing a dedicated cooling mechanism.

  The above-described control that can execute an appropriate downshift with excellent responsiveness even in a situation where the torque of the rotating electrical machine is insufficient is preferably applied during a power-off downshift. That is, the torque compensation unit performs control to compensate for the shortage when it is determined that the rotating electrical machine cannot output the required input torque during execution of the shift assist control during a power-off downshift. It is preferable.

Schematic diagram showing the schematic configuration of a vehicle drive device Block diagram showing schematic configuration of control device Schematic diagram showing an example of a shift map Flowchart showing the entire processing procedure of shift assist control The flowchart which shows the process sequence of a 1st burden determination process The flowchart which shows the process sequence of a 2nd burden determination process Time chart showing an example of the operating state of each part during shift assist control Time chart showing an example of the operating state of each part during shift assist control Time chart showing an example of the operating state of each part during shift assist control Time chart showing an example of the operating state of each part during shift assist control Time chart showing an example of the operating state of each part during shift assist control Schematic diagram showing another example of a shift map

  An embodiment of a control device according to the present invention will be described with reference to the drawings. The control device 3 according to the present embodiment targets the drive device 1 as a control target. Here, the driving device 1 is a vehicle driving device (hybrid vehicle driving device) for driving a vehicle (hybrid vehicle) including both the internal combustion engine 11 and the rotating electrical machine 12 as a driving force source of the wheels 15. . Hereinafter, the control device 3 according to the present embodiment will be described in detail.

1. Configuration of Drive Device A configuration of the drive device 1 to be controlled by the control device 3 will be described. As shown in FIG. 1, the drive device 1 according to the present embodiment includes a rotating electrical machine 12 in a power transmission path that connects the internal combustion engine 11 and the wheels 15, and shifts between the rotating electrical machine 12 and the wheels 15. A mechanism 13 is provided. That is, the drive device 1 includes a rotating electrical machine 12 and a transmission mechanism 13 in order from the internal combustion engine 11 side in a power transmission path that connects the internal combustion engine 11 and the wheels 15. These are accommodated in a drive unit case (not shown).

  The internal combustion engine 11 is a prime mover (gasoline engine or the like) that is driven by combustion of fuel inside the engine to extract power. The internal combustion engine 11 is drivingly connected to an input shaft I as an input member of the driving device 1. In this example, the output shaft of the internal combustion engine such as a crankshaft of the internal combustion engine 11 is drivingly connected so as to rotate integrally with the input shaft I. The internal combustion engine 11 is drivingly connected to the rotating electrical machine 12 via the input shaft I. “Drive coupling” means a state in which two rotating members are coupled so as to be able to transmit a driving force (synonymous with torque). This concept includes a state in which two rotating members are connected to rotate integrally, a state in which driving force is transmitted through one or more transmission members (shaft, gear mechanism, belt, etc.), etc. Is included.

  The rotating electrical machine 12 includes a rotor and a stator, and can perform both a function as a motor (electric motor) and a function as a generator (generator). The rotor of the rotating electrical machine 12 is drivingly connected so as to rotate integrally with the input shaft I. The rotating electrical machine 12 is electrically connected to a power storage device 25 (battery, capacitor, etc.) via an inverter device 24 (see FIG. 2). The rotating electrical machine 12 receives power from the power storage device 25 and performs powering or supplies the power generated by the torque of the internal combustion engine 11 to the power storage device 25 for storage. The input shaft I is drivably coupled to the speed change mechanism 13, and is a rotating member (an input member of the speed change mechanism 13) closest to the internal combustion engine 11 along the power transmission path in the speed change mechanism 13. In the present embodiment, the input shaft I corresponds to the “input side rotating member” in the present invention.

  In this embodiment, the speed change mechanism 13 is an automatic stepped speed change mechanism configured to be able to switch between a plurality of speed stages having different speed ratios (gear ratios). In order to form the plurality of shift stages, the transmission mechanism 13 includes a gear mechanism and a plurality of engagement devices (transmission engagement devices) that engage or disengage rotation elements of the gear mechanism. Each of these engagement devices is configured as a friction engagement device capable of transmitting torque by a friction force generated between engagement members engaged with each other. As these engagement devices, a wet multi-plate clutch (including a brake) or the like can be used. The engagement devices included in the transmission mechanism 13 include a first engagement device CL1, a second engagement device CL2,. In the present embodiment, the speed change mechanism 13 forms a target gear position at each time point with a specific two of the plurality of engaging devices in a direct engagement state and the other in a released state. In addition, it is good also as a structure which forms a target gear stage by making a specific one or three or more specific direct engagement states. In this way, the transmission mechanism 13 can switch a plurality of gear positions (change the gear ratio) by controlling the engagement states of the plurality of gear engagement devices.

  The speed change mechanism 13 changes the rotational speed of the input shaft I and transmits it to the output shaft O based on the speed ratio set for the formed speed stage. Here, the gear ratio is the ratio of the rotational speed of the input shaft I to the rotational speed of the output shaft O as the output side rotating member of the transmission mechanism 13. The output shaft O which is also an output member of the driving device 1 is drivingly connected to the two left and right wheels 15 via the differential gear device 14. Torque transmitted to the output shaft O is distributed by the differential gear unit 14 and transmitted to the two wheels 15. In this way, the drive device 1 can cause the vehicle to travel by transmitting the torque of one or both of the internal combustion engine 11 and the rotating electrical machine 12 to the wheels 15.

2. Configuration of Control Device A configuration of the control device 3 according to the present embodiment will be described. As shown in FIG. 2, the control device 3 according to the present embodiment includes a plurality of functional units, and mainly controls the rotating electrical machine 12 and the shift engagement devices (CL1, CL2,...). The plurality of functional units are configured to exchange information with each other. The control device 3 is configured to exchange information with the internal combustion engine control unit 21 that controls the internal combustion engine 11. The control device 3 is configured to be able to acquire information on detection results by the sensors Se1 to Se5 provided in each part of the vehicle.

  The first rotation sensor Se1 is a sensor that detects the rotation speed of the input shaft I (the internal combustion engine 11 and the rotating electrical machine 12). The second rotation sensor Se2 is a sensor that detects the rotation speed of the output shaft O. The control device 3 can derive the rotation speed and the vehicle speed of the wheel 15 based on the detection result by the second rotation sensor Se2. The accelerator opening detection sensor Se3 is a sensor that detects the accelerator opening. The charge state detection sensor Se4 is a sensor that detects an SOC (state of charge). The control device 3 can derive the amount of power stored in the power storage device 25 based on the detection result by the charge state detection sensor Se4. The lever position detection sensor Se5 is a sensor that detects the position of a shift lever (not shown). The position of the shift lever can be selected from, for example, a stop position (P range position), an automatic travel position (for example, D range position), a neutral position (N range position), and a manual travel position (for example, sports sequential position). Can be selected. Among these, in the present embodiment, it is assumed that the vehicle travels when the shift lever is in the automatic travel position or the manual travel position.

  The internal combustion engine control unit 21 controls the internal combustion engine 11. The internal combustion engine control unit 21 determines a target torque and a target rotation speed of the internal combustion engine 11, and controls the operation of the internal combustion engine 11 according to these control targets. In the present embodiment, the internal combustion engine control unit 21 can switch between torque control and rotational speed control of the internal combustion engine 11 in accordance with the traveling state of the vehicle. The torque control is a control for instructing a target torque to the internal combustion engine 11 and causing the torque of the internal combustion engine 11 to follow the target torque. The rotational speed control is a control for instructing a target rotational speed to the internal combustion engine 11 and determining a torque so that the rotational speed of the internal combustion engine 11 approaches the target rotational speed.

  The travel mode determination unit 31 is a functional unit that determines the travel mode of the vehicle. The travel mode determination unit 31 refers to, for example, a mode selection map (not shown), and determines a travel mode to be realized by the drive device 1 based on the vehicle speed, the accelerator opening, the power storage amount of the power storage device 25, and the like. . In the present embodiment, the driving modes that can be selected by the driving mode determination unit 31 include an electric driving mode (EV mode) and a hybrid driving mode (HEV mode). In the electric travel mode, in a state where fuel supply to the internal combustion engine 11 is stopped, the torque of the rotating electrical machine 12 is transmitted to the wheels 15 to cause the vehicle to travel. In the hybrid travel mode, the torque of both the internal combustion engine 11 and the rotating electrical machine 12 is applied to the wheel 15 while the internal combustion engine 11 outputs a positive torque (torque in a direction that accelerates the rotation of the wheel 15 in the forward direction of the vehicle). Transmit the vehicle to run. Note that a travel mode other than these may be selected.

  The transmission mode selection unit 32 is a functional unit that selects a transmission mode. The transmission mode selection unit 32 selects a transmission mode alternatively from the first transmission mode and the second transmission mode. In the present embodiment, the transmission mode selection unit 32 selects a transmission mode based on a command from the driver. Specifically, the transmission mode selection unit 32 selects the transmission mode based on the position of the shift lever detected by the lever position detection sensor Se5. Specifically, the shift mode selection unit 32 selects the first shift mode when the detected position of the shift lever is the automatic travel position, and selects the second shift mode when the detected position of the shift lever is the manual travel position. Select. In the present embodiment, the transmission mode selection unit 32 corresponds to the “mode selection unit” in the present invention.

  Here, the first speed change mode is a speed change mode in which the target speed change stage 33 (to be described later) automatically changes the target speed change (as a result, the speed change ratio is changed) according to a predetermined shift schedule. (Automatic shift mode). In the present embodiment, a shift map (see FIG. 3) defining a shift schedule is stored in storage means such as a memory provided in the control device 3. The shift map defines a shift schedule based on the relationship between the vehicle speed, the accelerator opening, the brake operation amount, and the target shift stage. This shift schedule is defined in consideration of at least bringing the fuel consumption (travel distance per unit capacity of fuel) close to the maximum value when the vehicle is traveling. On the other hand, the second shift mode is a shift mode in which the start condition of the shift control is different from the first shift mode in the present embodiment. In the present embodiment, based on the driver's intention, a shift mode (manually capable of changing the target gear stage (and thus changing the gear ratio)) can be manually changed regardless of the shift schedule defined in the shift map. Shift mode). When the second shift mode is realized, the shift command (upshift command or downshift command) is basically hydraulically controlled based on a predetermined shift lever operation by the driver while following the same shift schedule as the first shift mode. Is output to the unit 35.

  “Upshift” means a change of the target gear position to the high speed side (change to relatively reduce the gear ratio). That is, it means that the target gear position is changed to a gear position on the higher speed side than the gear position before the change (the gear ratio is made smaller than that before the change). “Downshift” means the change of the target gear position to the low speed side (change that relatively increases the gear ratio). In other words, it means that the target gear position is changed to a lower gear position than the gear position before the change (the gear ratio is made larger than before the change).

  The target shift speed determining unit 33 is a functional unit that determines the target shift speed according to the shift schedule defined in the shift map. The target shift speed determination unit 33 determines a target shift speed to be formed by the speed change mechanism 13 based on the vehicle speed and the accelerator opening with reference to, for example, a shift map shown in FIG. In the present embodiment, the target shift speed determining unit 33 determines one specific shift speed selected from the first speed to the sixth speed as the target shift speed. A plurality of shift lines are set in the shift map. When the vehicle speed and the accelerator opening change and the operating point on the shift map crosses the shift line, the target shift stage determination unit 33 changes the target shift stage. FIG. 3 shows an example in which both upshift and downshift are determined based on a single shift line for simplification. However, hysteresis is provided, and both shifts are individually increased. The determination may be made based on the shift line and the downshift line. When the target shift speed is changed, a shift command (upshift command or downshift command) corresponding to the change direction is output to the hydraulic control unit 35.

  The rotating electrical machine control unit 34 is a functional unit that controls the rotating electrical machine 12. The rotating electrical machine control unit 34 determines a target torque and a target rotational speed of the rotating electrical machine 12 and controls the operation of the rotating electrical machine 12 according to these control targets. In the present embodiment, the rotating electrical machine control unit 34 can switch between torque control and rotational speed control of the rotating electrical machine 12 according to the traveling state of the vehicle. The torque control is a control for instructing the rotary electric machine 12 with a target torque and causing the torque of the rotary electric machine 12 to follow the target torque. The rotational speed control is a control in which a target rotational speed is commanded to the rotating electrical machine 12 and torque is determined so that the rotational speed of the rotating electrical machine 12 approaches the target rotational speed.

  The torque that can be output by the rotating electrical machine 12 may be limited depending on the situation where the rotating electrical machine 12 is placed. For example, the rotating electrical machine 12 can output only torque within a range equal to or less than the maximum torque predetermined by the specification (concept toward both the positive direction and the negative direction). In addition, the rotating electrical machine 12 has only a torque within a range that is equal to or less than an upper limit torque that is determined based on a relationship with a maximum output that is determined in advance by specifications according to the rotation speed (a concept that is directed in both the positive and negative directions). Can be output. These maximum torque and upper limit torque may vary depending on the environmental temperature, the amount of power stored in the power storage device 25, and the like. For example, when the environmental temperature is equal to or lower than a predetermined low temperature threshold, the maximum torque and the upper limit torque can be reduced (on an absolute value basis). In addition, the maximum torque and the upper limit torque may be individually limited in the positive direction and the negative direction. For example, when the power storage amount of the power storage device 25 is equal to or less than a predetermined low power storage amount threshold value, only the maximum positive direction torque and the upper limit torque are reduced, and the power storage amount of the power storage device 25 is a predetermined high power storage amount threshold value. In this case, only the maximum torque and the upper limit torque in the negative direction can be reduced (on an absolute value basis). Note that the upper and lower limits of the torque that can be output by the rotating electrical machine 12 are indicated by broken lines in FIGS.

  The hydraulic control unit 35 is a functional unit that controls the supply of hydraulic pressure to each engagement device (CL1, CL2,...). The hydraulic pressure control unit 35 outputs a hydraulic pressure command to each engagement device according to the determined target shift speed, and controls the hydraulic pressure supplied to each engagement device via the hydraulic pressure control device 28. The hydraulic control unit 35 can continuously control the hydraulic pressure supplied to each engagement device with a proportional solenoid or the like in accordance with a hydraulic pressure command. Thereby, increase / decrease of the engagement pressure of each engagement apparatus is controlled continuously, and the engagement state of each engagement apparatus is controlled. For example, the hydraulic control unit 35 sets the target engagement device in the released state by setting the hydraulic pressure supplied to the target engagement device (target engagement device) to be less than the release boundary pressure. In addition, the hydraulic pressure control unit 35 sets the target engagement device in the direct engagement state by setting the supply hydraulic pressure to the target engagement device to be equal to or higher than the engagement boundary pressure. Further, the hydraulic control unit 35 sets the target engagement device in the slip engagement state by setting the hydraulic pressure supplied to the target engagement device to a slip engagement pressure that is greater than or equal to the release boundary pressure and less than the engagement boundary pressure.

  The “released state” means a state in which rotation and torque are not transmitted between the two engaging members engaged by the target engaging device. The “directly engaged state” means a state in which the two engaging members are engaged in a state of rotating integrally. The “slip engagement state” means a state in which the two engagement members are engaged so as to transmit torque in a state of having a differential rotation. In the slip engagement state of the target engagement device, torque is transmitted from the engagement member with the higher rotation speed toward the engagement member with the lower rotation speed while the two engagement members rotate relative to each other. Note that the magnitude of torque that can be transmitted in the engagement state of the target engagement device (concept including both the direct engagement state and the slip engagement state) is the hydraulic pressure supplied to the target engagement device (target It depends on the engagement pressure of the engagement device. The magnitude of the torque at this time is defined as the transmission torque capacity of the target engagement device. The transmission torque capacity of each engagement device can be continuously controlled according to the increase or decrease of the supply hydraulic pressure.

  In the present embodiment, when receiving a shift command from the target shift speed determination unit 33, the hydraulic control unit 35 supplies the hydraulic pressure supplied to the engagement devices CL1, CL2,... According to the changed target shift speed. To control. At this time, the hydraulic control unit 35 sets one of the engagement devices that were in the direct engagement state before the shift to the release state and one of the engagement devices that was in the release state before the shift. Is finally brought into a direct engagement state through a slip engagement state. In the following description, it is assumed that the first engagement device CL1 is newly released after the shift speed is changed and the second engagement device CL2 is newly engaged in the replacement gear shift as described above. Shall be assumed. The hydraulic control unit 35 controls the hydraulic pressure supplied to each engagement device, and controls the state of each engagement, thereby switching the gear stage realized by the transmission mechanism 13.

  The shift assist control unit 41 increases or decreases the torque of the rotating electrical machine 12 transmitted to the input shaft I during execution of shift control for switching the shift speed realized by the transmission mechanism 13 to rotate the input shaft I. This is a functional unit that executes shift assist control for increasing or decreasing the speed. The shift assist control unit 41 increases or decreases the torque of the rotating electrical machine 12 according to the shift speed switching direction (change ratio changing direction). Here, the virtual rotational speed of the input shaft I determined according to the vehicle speed and the gear ratio is defined as a synchronous rotational speed Ns, and the synchronous rotational speed Ns before and after the shift is defined as the synchronous rotational speed Nsa before the shift and the synchronous rotation after the shift, respectively. The speed is defined as Nsb. Then, at the time of downshift, the post-shift synchronous rotational speed Nsb becomes higher than the pre-shift synchronous rotational speed Nsa. On the other hand, the reverse is the reverse, and the latter is lower than the former.

  Therefore, the shift assist control unit 41 increases the torque of the rotating electrical machine 12 transmitted to the input shaft I during the downshift and increases the rotation speed of the input shaft I by the shift assist control. Here, the increase in torque of the rotating electrical machine 12 represents an increase on the absolute basis (change in the positive direction). For this purpose, a larger positive torque is output from a state where the rotating electrical machine 12 outputs a positive torque, or a smaller negative torque or a smaller torque is output from a state where the rotating electrical machine 12 outputs a negative torque. It includes outputting zero or more torque. On the other hand, the shift assist control unit 41 decreases the rotational speed of the input shaft I by reducing the torque of the rotating electrical machine 12 transmitted to the input shaft I during upshifting. Here, the decrease in the torque of the rotating electrical machine 12 represents a decrease on the absolute basis (change in the negative direction). This can be achieved by causing the rotating electrical machine 12 to output a positive torque with a smaller positive torque or a torque of zero or less, or from the state where the rotating electrical machine 12 is outputting a negative torque. It includes outputting a large negative torque.

  The shift assist control unit 41 can quickly bring the actual rotational speed of the input shaft I closer to the post-shift synchronous rotational speed Nsb by executing such shift assist control when executing the shift control. Therefore, it is possible to execute shift control with excellent responsiveness.

  Whether or not the rotating electrical machine 12 can output the necessary input torque Tn for increasing or decreasing the rotational speed of the input shaft I according to a predetermined target rotational speed change rate At. It is a function part which determines. As described above, the torque that can be output by the rotating electrical machine 12 may be limited. Therefore, the possibility determination unit 42 determines whether or not the necessary input torque Tn can be reliably output in relation to the torque limitation of the rotating electrical machine 12. Further, the possibility determination unit 42 determines whether or not the required input torque Tn can be output in cooperation between the rotating electrical machine 12 and the internal combustion engine 11 under a predetermined condition. Further, the possibility determining unit 42 indicates that the rotating electrical machine 12 generates a lower limit input torque To for increasing or decreasing the rotation speed of the input shaft I according to a predetermined lower limit rotation speed change rate Ao under a predetermined condition. It is determined whether or not output is possible. Refer to the flowcharts of FIGS. 4 to 6 for details of the functions of the possibility determination unit 42, the necessary input torque Tn, the lower limit input torque To, the target rotational speed change rate At, the lower limit rotational speed change rate Ao, and the like. Will be described later.

  The torque compensation unit 43 is a functional unit that compensates for a shortage with respect to the required input torque Tn in the shift assist control when it is determined that the rotary electric machine 12 cannot output the required input torque Tn. The torque compensation unit 43 is at least one of the output torque of the internal combustion engine 11 and the transmission torque transmitted by the shift engagement device (here, the second engagement device CL2 newly engaged during the shift control). Is used to compensate for the shortage with respect to the required input torque Tn. At this time, the torque compensation unit 43 does not make the load ratio of the output torque of the internal combustion engine 11 and the transmission torque by the second engagement device CL2 uniform (unified) regardless of the situation, but according to the speed change mode. Variable. The torque compensation unit 43 appropriately compensates the shortage with respect to the necessary input torque Tn using at least one of the output torque of the internal combustion engine 11 and the transmission torque of the second engagement device CL2 according to the speed change mode. The auxiliary subject determining unit 44 and the burden determining unit 45 are provided.

  The auxiliary main body determining unit 44 is a main body (referred to as “auxiliary main body Sa”) that compensates for the shortage with respect to the required input torque Tn in the shift assist control when it is determined that the rotating electrical machine 12 cannot output the required input torque Tn. It is a functional part to be determined. The auxiliary main body determination unit 44 selects the auxiliary main body Sa from the internal combustion engine 11 and the shift engagement device (here, the second engagement device CL2) according to the shift mode realized at the start of the shift assist control. decide. That is, the auxiliary subject determining unit 44 does not determine the auxiliary subject Sa uniformly regardless of the situation, but variably determines the auxiliary subject Sa according to the shift mode.

  The load determining unit 45 is a functional unit that determines a torque load when the rotational speed of the input shaft I is increased or decreased in the shift assist control. The load determination unit 45 determines whether the rotating electrical machine 12 and the auxiliary main body Sa (the internal combustion engine 11 and / or the second connection) are necessary based on the determination result by the possibility determination unit 42, the determination items by the auxiliary main body determination unit 44, and the like. The torque burden with the combined device CL2) is determined. Since the auxiliary subject determination unit 44 and the load determination unit 45 work cooperatively, the shortage with respect to the required input torque Tn is determined according to the speed change mode, and the output torque of the internal combustion engine 11 and the transmission torque of the second engagement device CL2. Is supplemented with at least one of Details of the functions of the torque compensation unit 43 (auxiliary subject determination unit 44 and load determination unit 45) will be described later with reference to the flowcharts of FIGS.

3. Contents of Shift Assist Control Specific contents of the shift assist control according to the present embodiment will be described. In the present embodiment, the shift assist control (power off down shift assist control) during downshift (power off downshift) during coasting will be particularly described. Note that “coast running” means running in a state where the accelerator opening is equal to or less than a predetermined reference opening (can be set to an arbitrary value such as 1 to 5%, for example). Each process in the shift assist control described below includes the shift assist control unit 41, the possibility determination unit 42, and the torque compensation unit 43 (auxiliary subject determination unit 44 and load determination unit 45) as the core. It is executed by the function unit. In the following description, in order to simplify the description, the transmission torque capacity of the second engagement device CL2 is described as a capacity in terms of the input shaft I. The transmission torque capacity in terms of the input shaft I is after torque conversion based on the position of the input shaft I according to the position of the second engagement device CL2 in the power transmission path connecting the input shaft I and the output shaft O. Torque (transmission torque capacity).

  In the present embodiment, it is assumed that the position of the shift lever is an automatic travel position or a manual travel position, and at least the vehicle is traveling. In this case, the vehicle is traveling in the first speed change mode or the second speed change mode. In this state, as shown in FIG. 4, it is determined whether or not there has been a downshift request (step # 01). That is, it is determined whether or not a downshift command is output based on the determination result of the target shift stage determination unit 33 according to the shift schedule defined in the shift map or the shift lever operation by the driver. When there is no downshift request, that is, when there is no shift request itself or when there is an upshift request (# 01: No), the shift assist control (power-off downshift assist control) is once terminated and again Shift assist control is started.

  If there is a downshift request (# 01: Yes), it is next determined whether or not the requested driving force D is negative (D <0) (# 02). Here, the required driving force D is a torque required to drive the vehicle when the sign is positive (D> 0). Therefore, the required driving force D being negative means that torque (running resistance) that decelerates the vehicle is acting on the vehicle. If the required driving force D is greater than or equal to zero (# 02: No), the shift assist control (power-off down shift assist control) is once ended and the shift assist control is started again.

  If the required driving force D is negative (# 02: Yes), the transmission mode selection unit 32 then determines which transmission mode is realized at that time (# 03). Specifically, it is determined which one of the first shift mode and the second shift mode is selected based on the shift lever position information detected by the lever position detection sensor Se5. If the first speed change mode is selected (# 04: Yes), the auxiliary main body determining unit 44 or the like determines the second engagement device CL2 as the auxiliary main body Sa with conditions (# 05), and determines the burden. The first burden determination process is executed by the unit 45 or the like (# 06). On the other hand, if the second speed change mode is selected (# 04: No), the auxiliary main body determination unit 44 or the like may conditionally include the internal combustion engine 11 (in some cases, the second engagement device CL2 may also be included). ) Is determined as the auxiliary subject Sa (# 07), and the second load determining process is executed by the load determining unit 45 or the like (# 08).

  As shown in FIG. 5, in the first load determination process, first, the required input torque Tn is calculated by the possibility determination unit 42 (# 11). Here, the required input torque Tn is a torque that needs to be transmitted to the input shaft I in order to increase the rotational speed of the input shaft I in accordance with a predetermined target rotational speed change rate At. The target rotational speed change rate At of the input shaft I is set so that the shift control (in particular, the so-called inertia phase in this case) can be completed within a predetermined target shift time Pt. The target rotational speed change rate At is calculated based on the difference between the synchronous rotational speeds Ns before and after the shift and the target shift time Pt. Specifically, a value obtained by subtracting the pre-shift synchronous rotation speed Nsa from the post-shift synchronous rotation speed Nsb is calculated by dividing the value by the target shift time Pt. The required input torque Tn is calculated based on the target rotational speed change rate At calculated in this way and the total inertia J (the sum of the rotor inertia of the rotating electrical machine 12 and the inertia of the internal combustion engine 11). Specifically, it is calculated by multiplying the total inertia J and the target rotational speed change rate At.

  Next, the possibility determination unit 42 calculates a rotating electrical machine assistable torque Tam (# 12). Here, the rotating electrical machine assistable torque Tam is a torque that can be used for assisting the shift by increasing the rotational speed of the input shaft I among the torques that can be output by the rotating electrical machine 12. The rotating electrical machine assistable torque Tam is calculated based on the rotating electrical machine torque Tm, the required driving force D, and the friction torque Tf of the internal combustion engine 11. The rotating electrical machine torque Tm is the smaller of the maximum torque for the rotating electrical machine 12 and the upper limit torque corresponding to the post-shift synchronous rotation speed Nsb. The friction torque Tf is a sliding resistance or the like when the output shaft (crankshaft or the like) of the internal combustion engine 11 rotates, and takes a negative value (Tf <0). The rotating electrical machine assistable torque Tam is calculated by subtracting the required driving force D from the rotating electrical machine torque Tm and adding the friction torque Tf taking a negative value.

  Next, the possibility determination unit 42 determines whether or not the rotating electrical machine 12 can output the required input torque Tn. Here, the rotating electrical machine 12 can output the required input torque Tn in addition to the torque for absorbing the required driving force D that takes a negative value and the torque for compensating the friction torque Tf within the torque limit range. It is determined whether or not. Specifically, it is determined whether or not the rotating electrical machine assistable torque Tam is equal to or greater than the required input torque Tn (# 13).

  When it is determined that the rotating electrical machine 12 can output the required input torque Tn, that is, the rotating electrical machine assistable torque Tam is equal to or greater than the required input torque Tn (# 13: Yes), the load determining unit 45 causes the torque load pattern to be Is determined as the basic burden pattern (# 17). The basic burden pattern is such that the main body that bears the required input torque Tn is only the rotating electrical machine 12. That is, in the basic load pattern, the entire required input torque Tn is output to the rotating electrical machine 12.

  In this basic load pattern, the internal combustion engine 11 applies a resistance equivalent to the friction torque Tf to the input shaft I. The transmission torque capacity of the second engagement device CL2 is a value corresponding to the required driving force D. When the required driving force D takes a negative value as in this example, the sign is inverted (−D). The rotating electrical machine 12 includes a torque for maintaining the state in which the required driving force D is transmitted to the wheels 15, a necessary input torque Tn for performing shift assist, and a torque (-Tf) for compensating the friction torque Tf. The total torque is output. As a result, as shown in FIG. 7, the rotational speed of the input shaft I is changed along with the target rotational speed change rate At in the state where the torque transmitted to the wheels 15 is maintained at the required driving force D. It rises to Nsb. That is, a downshift with excellent responsiveness is realized within the target shift time Pt.

  When it is determined that the rotating electrical machine 12 cannot output the required input torque Tn, that is, the rotating electrical machine assistable torque Tam is less than the required input torque Tn (# 13: No), the possibility determining unit 42 determines the limit. The rotational speed change rate Ar is calculated (# 14). The limit rotational speed change rate Ar is calculated based on the rotating electric machine assistable torque Tam and the total inertia J. Specifically, it is calculated by dividing the rotating electric machine assistable torque Tam by the total inertia J.

  Next, the possibility determination unit 42 determines whether the limit rotational speed change rate Ar is equal to or greater than the lower limit rotational speed change rate Ao (# 15). Here, the lower limit rotational speed change rate Ao of the input shaft I is set so that the shift control (here, in particular, the so-called inertia phase) can be completed within a predetermined upper limit shift time Pu. The upper limit shift time Pu is determined such that the heat generation amount of the second engagement device CL2 that is brought into the slip engagement state during shift control (so-called inertia phase) is equal to or less than a predetermined allowable heat generation amount Qp. Yes. Such an upper limit shift time Pu can be empirically obtained in advance based on, for example, a preliminary experiment for verifying the heat resistance performance of the second engagement device CL2. The lower limit rotational speed change rate Ao is calculated based on the difference between the synchronous rotational speeds Ns before and after the shift and the upper limit shift time Pu. Specifically, the value obtained by subtracting the synchronous rotational speed Nsa before shifting from the synchronous rotational speed Nsb after shifting is calculated by dividing the value by the upper limit shifting time Pu.

  In the present embodiment, the torque required to be transmitted to the input shaft I in order to increase the rotational speed of the input shaft I according to the lower limit rotational speed change rate Ao is the lower limit input torque To. Therefore, determining whether the limit rotational speed change rate Ar is equal to or higher than the lower limit rotational speed change rate Ao is equivalent to determining whether the rotating electrical machine 12 can output the lower limit input torque To. is there. Here, it is determined whether or not the rotating electrical machine 12 can output the lower limit input torque To in addition to the torque for absorbing the required driving force D taking a negative value and the torque for compensating the friction torque Tf. Is equivalent to

  When the rotating electrical machine 12 can output the lower limit input torque To, that is, when it is determined that the limit rotational speed change rate Ar is equal to or higher than the lower limit rotational speed change rate Ao (# 15: Yes), the load determining unit 45 The burden pattern is determined as the first special burden pattern (# 18). The first special burden pattern is such that only the rotating electric machine 12 is a main body that bears a part of the necessary input torque Tn in a state where the entire necessary input torque Tn is not satisfied. In other words, in the first special burden pattern, the rotating electrical machine assistable torque Tam that is greater than or equal to the lower limit input torque To and less than the required input torque Tn is output to the rotating electrical machine 12.

  In the first special burden pattern, the internal combustion engine 11 applies a resistance equivalent to the friction torque Tf to the input shaft I. The transmission torque capacity of the second engagement device CL2 is a required driving force D equivalent value (−D). The rotating electrical machine 12 is a torque for maintaining the state where the required driving force D is transmitted to the wheel 15, a rotating electrical machine assistable torque Tam for partially performing shift assist, and a torque for compensating the friction torque Tf. The total torque with (−Tf) is output. As a result, as shown in FIG. 8, in a state where the torque transmitted to the wheel 15 is maintained at the required driving force D, the limit rotational speed that is greater than the lower limit rotational speed change rate Ao and less than the target rotational speed change rate At. At the rate of change Ar, the rotational speed of the input shaft I increases to the synchronized rotational speed Nsb after the shift. That is, a downshift with relatively excellent responsiveness is realized while suppressing a shift shock.

  When it is determined that the rotating electrical machine 12 cannot output the lower limit input torque To, that is, the limit rotational speed change rate Ar is less than the lower limit rotational speed change rate Ao (# 15: No), the load determining unit 45 The engagement device assist torque Tac is calculated (# 16). The engagement device assist torque Tac is a portion of the transfer torque capacity of the second engagement device CL2 that is used to increase the rotation speed of the input shaft I to perform shift assist. The engagement device assist torque Tac in the first load determination process is calculated based on the limit rotational speed change rate Ar, the lower limit rotational speed change rate Ao, and the total inertia J. Specifically, it is calculated by multiplying the value obtained by subtracting the lower limit rotational speed change rate Ao from the limit rotational speed change rate Ar and the total inertia J.

  Then, the load determining unit 45 determines the torque load pattern as the second special load pattern (# 19). In the second special burden pattern, the main body that bears a part of the necessary input torque Tn is the rotating electrical machine 12 and the second engagement device CL2 in a state where the entire necessary input torque Tn is not satisfied. That is, in the second special burden pattern, the auxiliary main body determining unit 44 determines the second engagement device CL2 as a single auxiliary main body Sa for assisting the shift assist by the rotating electrical machine 12. At this time, as is apparent from the above description, the second engagement device CL2 determines that the rotating electrical machine 12 has determined that the lower limit input torque To cannot be output (# 15: No). As determined.

  In this second special load pattern, the internal combustion engine 11 causes a resistance equivalent to the friction torque Tf to act on the input shaft I. The rotating electrical machine 12 is a torque for maintaining the state where the required driving force D is transmitted to the wheel 15, a rotating electrical machine assistable torque Tam for partially performing shift assist, and a torque for compensating the friction torque Tf. The total torque with (−Tf) is output. The transmission torque capacity of the second engagement device CL2 is a value obtained by adding the engagement device assist torque Tac to the required driving force D equivalent value (−D). As a result, as shown in FIG. 9, the rotational speed of the input shaft I increases to the post-shift synchronous rotational speed Nsb along the lower limit rotational speed change rate Ao that is larger than the limit rotational speed change rate Ar. In this case, compared with the case where the second engagement device CL2 does not function as the auxiliary main body Sa (see the rotation speed indicated by the one-dot chain line of the input shaft I), thermal degradation of the second engagement device CL2 is suppressed. On the other hand, downshift with relatively excellent response is realized. Note that the torque transmitted to the wheel 15 is slightly lower than the required driving force D as the transmission torque capacity of the second engagement device CL2 is increased by the engagement device assist torque Tac. However, in the present embodiment, priority is given to suppression of thermal degradation of the second engagement device CL2 by shortening the shift control time.

  As shown in FIG. 6, in the second load determination process, the required input torque Tn is calculated (# 21), the rotating electrical machine assistable torque Tam is calculated (# 22), and the rotating electrical machine assistable torque Tam is calculated as the required input torque. It is determined whether it is equal to or greater than Tn (# 23). When it is determined that the rotating electrical machine assistable torque Tam is equal to or greater than the required input torque Tn (# 23: Yes), the torque load pattern is determined as the basic load pattern (# 27). These processes are the same as the processes in steps # 11 to # 13 and # 17 in the first load determination process.

  When it is determined that the rotating electrical machine 12 cannot output the required input torque Tn, that is, the rotating electrical machine assistable torque Tam is less than the required input torque Tn (# 23: No), the possibility determination unit 42 determines whether the internal combustion engine The engine assist torque Tae is calculated (# 24). Here, the internal combustion engine assist torque Tae is a torque that can be used to perform a shift assist by increasing the rotational speed of the input shaft I among the torques that the internal combustion engine 11 can additionally output. The internal combustion engine assist torque Tae is calculated based on the internal combustion engine maximum increase torque Tie and the friction torque Tf. The internal combustion engine maximum increase torque Tie is the maximum value of torque that the internal combustion engine 11 can additionally output. Specifically, the internal combustion engine assist torque Tae is calculated by adding a negative friction torque Tf to the internal combustion engine maximum increase torque Tie.

  Next, the possibility determination unit 42 determines whether or not the rotary electric machine 12 and the internal combustion engine 11 can output the necessary input torque Tn in cooperation. Here, it is determined whether or not the internal combustion engine 11 can output an amount that is insufficient with only the rotating electrical machine assistable torque Tam with respect to the required input torque Tn. This determination is made based on the internal combustion engine assist torque Tae, the required input torque Tn, and the rotating electric machine assistable torque Tam. Specifically, it is determined whether or not the internal combustion engine assist torque Tae is equal to or greater than a value (necessary difference value) obtained by subtracting the rotating electrical machine assistable torque Tam from the required input torque Tn (# 25).

  When it is determined that the internal combustion engine 11 can output the shortage with respect to the necessary input torque Tn, that is, the internal combustion engine assist torque Tae is equal to or greater than the necessary difference value (# 25: Yes), the burden determining unit 45 The torque burden pattern is determined as the third special burden pattern (# 28). In the third special burden pattern, the main body that bears the necessary input torque Tn is the rotating electrical machine 12 and the internal combustion engine 11. That is, in the third special burden pattern, the auxiliary main body determining unit 44 includes the internal combustion engine 11 in the auxiliary main body Sa for assisting the shift assist by the rotating electrical machine 12. In the third special burden pattern, the entire required input torque Tn is output to the rotating electrical machine 12 and the internal combustion engine 11 that function in a cooperative manner.

  In the third special burden pattern, the internal combustion engine 11 outputs a value (necessary difference value) obtained by subtracting the rotating electrical machine assistable torque Tam from the necessary input torque Tn. Note that the output torque of the internal combustion engine 11 is the one after the friction torque Tf is canceled. The rotating electrical machine 12 outputs the total torque of the torque for maintaining the state where the required driving force D is transmitted to the wheels 15 and the rotating electrical machine assistable torque Tam for partially performing the shift assist. The transmission torque capacity of the second engagement device CL2 is a required driving force D equivalent value (−D). As a result, as shown in FIG. 10, the rotational speed of the input shaft I is changed along with the target rotational speed change rate At while the torque transmitted to the wheel 15 is maintained at the required driving force D, and the post-shift synchronous rotational speed. It rises to Nsb. That is, a downshift with excellent responsiveness is realized within the target shift time Pt. As the internal combustion engine 11 outputs a predetermined torque, the fuel consumption slightly decreases. However, in the present embodiment, since the second shift mode is shift control mainly based on the driver's intention, priority is given to improving the downshift response as much as possible.

  If it is determined that the required input torque Tn cannot be output even when the rotating electrical machine 12 and the internal combustion engine 11 cooperate, that is, the internal combustion engine assist torque Tae is less than the above required difference value (# 25: No) ), The engagement device assist torque Tac is calculated by the load determination unit 45 (# 26). The engagement device assist torque Tac is a portion of the transfer torque capacity of the second engagement device CL2 that is used to increase the rotation speed of the input shaft I to perform shift assist. The engagement device assist torque Tac in the second load determination process is calculated based on the necessary input torque Tn, the rotating electric machine assistable torque Tam, and the internal combustion engine assist torque Tae. Specifically, it is calculated by subtracting both the rotating electric machine assistable torque Tam and the internal combustion engine assist torque Tae from the necessary input torque Tn.

  Then, the load determining unit 45 determines the torque load pattern as the fourth special load pattern (# 29). In the fourth special burden pattern, the main body that bears the necessary input torque Tn is the rotating electrical machine 12, the internal combustion engine 11, and the second engagement device CL2. That is, in the fourth special burden pattern, the auxiliary main body determining unit 44 further includes the second engagement device CL2 in addition to the internal combustion engine 11 as an auxiliary main body Sa for assisting the shift assist by the rotating electrical machine 12. In the fourth special burden pattern, all of the necessary input torque Tn is output to the rotating electric machine 12, the internal combustion engine 11, and the second engagement device CL2 that function cooperatively.

  In the fourth special burden pattern, the internal combustion engine 11 outputs the internal combustion engine assist torque Tae. The internal combustion engine assist torque Tae is obtained as the friction torque Tf (<0) is canceled (Tae = Tie + Tf). The rotating electrical machine 12 outputs the total torque of the torque for maintaining the state where the required driving force D is transmitted to the wheels 15 and the rotating electrical machine assistable torque Tam for partially performing the shift assist. The transmission torque capacity of the second engagement device CL2 is a value obtained by adding the engagement device assist torque Tac to the required driving force D equivalent value (−D). As a result, as shown in FIG. 11, the rotational speed of the input shaft I increases to the post-shift synchronous rotational speed Nsb along the target rotational speed change rate At. That is, a downshift with excellent responsiveness is realized within the target shift time Pt. As the internal combustion engine 11 outputs a predetermined torque, the fuel consumption slightly decreases. Further, as the transmission torque capacity of the second engagement device CL2 is increased by the engagement device assist torque Tac, the torque transmitted to the wheel 15 is slightly lower than the required driving force D. However, in the present embodiment, since the second shift mode is shift control mainly based on the driver's intention, priority is given to improving the downshift response as much as possible.

  As described above, according to the control device 3 according to the present embodiment, the auxiliary main body Sa is set according to the control characteristics of the first shift mode that is the automatic shift mode and the second shift mode that is the manual shift mode. Can be determined appropriately. Then, according to the control characteristics of each shift mode, the shortage with respect to the required input torque Tn is converted into the output torque of the internal combustion engine 11 and the shift engagement device (here, the second engagement device CL2) according to the shift mode. ) Can be appropriately compensated using at least one of the transmission torques. Therefore, even in a situation where the torque of the rotating electrical machine 12 that can be used for the shift assist is insufficient, the control device 3 that can execute an appropriate downshift with excellent responsiveness can be realized. In particular, considering the fuel economy during vehicle travel and suppression of shift shock, etc., the overall control characteristics related to fuel consumption, shift shock, responsiveness, etc. during power-off downshift control are kept high depending on the situation. can do.

4). Other Embodiments Finally, other embodiments of the control device according to the present invention will be described. Note that the configurations disclosed in the following embodiments can be applied in combination with the configurations disclosed in other embodiments as long as no contradiction arises.

(1) In the above embodiment, the second speed change mode is a mode in which the start condition of the speed change control is different from that of the first speed change mode, specifically, the first speed change mode is the automatic speed change mode and the second speed change mode. The configuration in which the shift mode is the manual shift mode has been described as an example. However, the embodiment of the present invention is not limited to this. When both the first shift mode and the second shift mode are automatic shift modes, for example, shift maps (shift schedules) referred to in each shift mode may be different. For example, as shown in FIG. 12, the shift schedule (b) in the second shift mode is such that the target shift stage for the vehicle speed is set to the lower vehicle speed side relative to the shift schedule (a) in the first shift mode. It may be said. In such a configuration, the second shift mode is a mode in which the start condition of the shift control is different from that of the first shift mode, and acceleration response at the time of downshift is higher than that of the first shift mode.

  Alternatively, the second shift mode may be a mode in which the processing content of the shift control is different from the first shift mode. When both the first shift mode and the second shift mode are automatic shift modes that refer to a common shift map (shift schedule), the subject that executes shift assist control is different from the beginning (the basic load pattern is different). ) May be assumed. For example, in the second speed change mode, the internal combustion engine 11 may output a certain amount of torque from the beginning, and the rotary electric machine 12 and the internal combustion engine 11 may cooperate to execute the shift assist control from the beginning. In such a configuration, the second speed change mode is a mode in which the time required for the control for the downshift is shorter than the first speed change mode.

  It should be noted that the first shift mode and the second shift mode may have different shift control start conditions and different processing contents. Even in these configurations, the auxiliary main body Sa can be appropriately determined according to the control characteristics of the first shift mode and the second shift mode in which at least one of the shift control start condition and the processing content is different from each other. Therefore, even in a situation where the torque of the rotating electrical machine 12 that can be used for the shift assist is insufficient, the control device 3 that can execute an appropriate downshift with excellent responsiveness can be realized.

(2) In the above embodiment, if the rotating electrical machine 12 cannot output the required input torque Tn when the first speed change mode is selected, the lower limit input torque To cannot be output. The configuration in which the two-engagement device CL2 is the auxiliary main body Sa has been described as an example. However, the embodiment of the present invention is not limited to this. For example, in such a case, the second engagement device CL2 may be used as the auxiliary main body Sa unconditionally regardless of the relationship with the lower limit input torque To. In this case, the engagement device assist torque Tac can be calculated based on the required input torque Tn and the rotating electric machine assistable torque Tam. Specifically, it can be calculated by subtracting the rotating electric machine assistable torque Tam from the necessary input torque Tn. Thus, priority may be given to improving the downshift responsiveness by allowing a shift shock to some extent.

(3) In the above embodiment, when the required input torque Tn cannot be output even when the rotary electric machine 12 and the internal combustion engine 11 cooperate when the second speed change mode is selected, in addition to the internal combustion engine 11, further The configuration in which the second engagement device CL2 is also included in the auxiliary main body Sa has been described as an example. However, the embodiment of the present invention is not limited to this. For example, even in such a case, only the internal combustion engine 11 may be configured as the auxiliary main body Sa. That is, the second engagement device CL2 may not be included in the auxiliary main body Sa, and the shift assist may be performed only within the range of torque that can be output by the rotary electric machine 12 and the internal combustion engine 11 in cooperation. In this way, it may be possible to give priority to the suppression of the occurrence of shift shock by allowing a decrease in downshift responsiveness to some extent.

(4) In the above-described embodiment, the description has been made on the assumption that the shift mode selection by the driver and the shift command in the manual shift mode are performed based on the shift lever operation. However, the embodiment of the present invention is not limited to this. For example, it is good also as a structure performed based on input operation with respect to the button etc. which were provided in hardware or software. That is, any configuration may be employed as long as the driver's intention to shift or select can be input to the control device 3. The same applies to the selection of the travel mode.

(5) In the above embodiment, the drive device 1 to be controlled by the control device 3 has been described by taking the configuration shown in FIG. 1 as an example. However, the embodiment of the present invention is not limited to this. The drive device 1 may have any specific configuration as long as the rotating electrical machine 12 and the speed change mechanism 13 are provided in order from the internal combustion engine 11 side in the power transmission path connecting the internal combustion engine 11 and the wheels 15. . For example, the drive device 1 may be configured to include a disconnecting engagement device that selectively connects the internal combustion engine 11 and the rotating electrical machine 12 to each other. Moreover, it is good also as a structure provided with the fluid coupling (for example, torque converter etc.) which has the engaging apparatus for fastening between the rotary electric machine 12 and the speed change mechanism 13. FIG. Alternatively, a dedicated transmission engagement device may be provided at any position between the rotating electrical machine 12 and the differential gear device 14.

(6) In the above-described embodiment, an example in which the speed change mechanism 13 is an automatic stepped speed change mechanism configured to be able to switch a plurality of speed stages (change the speed ratio in stages) has been described. As this automatic stepped transmission mechanism, a type including a planetary gear mechanism and a hydraulic clutch, a type called a so-called dual clutch type, or the like can be used. However, the embodiment of the present invention is not limited to this. The speed change mechanism 13 may have any specific configuration as long as the speed change ratio can be changed by controlling the engagement state of the speed change engagement device provided in the speed change mechanism 13. For example, the transmission mechanism 13 may be configured as an automatic continuously variable transmission mechanism with a clutch.

(7) Regarding other configurations as well, the embodiments disclosed herein are illustrative in all respects, and the embodiments of the present invention are not limited thereto. In other words, configurations that are not described in the claims of the present application can be modified as appropriate without departing from the object of the present invention.

  INDUSTRIAL APPLICABILITY The present invention can be used for a control device that controls a drive device for a 1-motor parallel type hybrid vehicle.

1: Drive device (vehicle drive device)
3: Control device 11: Internal combustion engine 12: Rotating electrical machine 13: Transmission mechanism 15: Wheel 32: Transmission mode selection unit (mode selection unit)
41: Shift assist control unit 42: Possibility determination unit 43: Torque compensation unit 44: Auxiliary subject determination unit 45: Load determination unit I: Input shaft (input side rotating member)
CL1: First engagement device (shifting engagement device)
CL2: Second engagement device (shifting engagement device)
Ns: Synchronous rotational speed Nsa: Pre-shift synchronous rotational speed Nsb: Post-shift synchronous rotational speed ΔNs: Difference between pre-shift synchronous rotational speed and post-shift synchronous rotational speed At: Target rotational speed change rate Ao: Lower limit rotational speed change rate Pt : Target shift time Pu: upper limit shift time Tn: required input torque To: lower limit input torque Tam: rotating electric machine assistable torque Tae: internal combustion engine assist torque Tac: engagement device assist torque Qp: allowable heat generation amount

Claims (6)

A rotating electrical machine and a speed change mechanism are provided in order from the side of the internal combustion engine on a power transmission path connecting the internal combustion engine and the wheels, and the state of engagement of the speed change engagement device provided in the speed change mechanism is controlled. A control device for controlling a vehicle drive device in which the speed change mechanism is configured to change a gear ratio;
Shift assist control for increasing the rotational speed of the input-side rotating member by increasing the torque of the rotating electrical machine transmitted to the input-side rotating member of the transmission mechanism during a downshift that is changed to increase the gear ratio. A shift assist control unit for executing
A possibility determination unit that determines whether or not the rotating electrical machine can output the necessary input torque for increasing the rotation speed of the input side rotation member according to a predetermined target rotation speed change rate;
A mode selection unit that selectively selects a shift mode from a first shift mode and a second shift mode in which at least one of the downshift start condition and the processing content is different from the first shift mode;
When it is determined that the required electric torque cannot be output by the rotating electrical machine, the shortage with respect to the required input torque in the shift assist control is determined based on the output torque of the internal combustion engine and the gear for shifting. A torque compensation unit that compensates using at least one of transmission torques by the engagement device;
A control device comprising: The first speed change mode is an automatic speed change mode and the second speed change mode is a manual speed change mode, or the second speed change mode requires less time for control for the downshift than the first speed change mode. The short mode or the acceleration response at the time of the downshift is a mode higher than the first shift mode,
The torque compensation unit compensates for the shortage using the transmission torque of the gear shift engagement device when the first shift mode is selected, and at least compensates for the shortage when the second shift mode is selected. The control device according to claim 1, wherein compensation is performed using output torque. The possibility determination unit further determines whether or not the required input torque can be output in cooperation with the rotating electrical machine and the internal combustion engine,
When the second gear mode is selected, the torque compensation unit determines that the required input torque cannot be output even if the rotating electrical machine and the internal combustion engine cooperate with each other, and the gear shift engagement device The control device according to claim 2, wherein the shortage is compensated by further using a transmission torque generated by the control. The possibility determination unit further determines whether or not the rotating electrical machine can output a lower limit input torque for increasing the rotation speed of the input side rotation member according to a predetermined lower limit rotation speed change rate. And
The torque compensation unit uses the torque transmitted by the gear shift engagement device to determine whether the shortage of the rotating electrical machine is determined to be impossible to output the lower limit input torque when the first speed change mode is selected. The control device according to claim 2 or 3, which compensates for the minute. The rotational speed of the input side rotating member determined according to the vehicle speed and the gear ratio is the synchronous rotational speed,
The lower limit rotational speed change rate is the difference between the synchronous rotational speeds before and after the change of the gear ratio, and the heat generation amount of the shift engagement device slipped when the gear ratio is changed is less than or equal to a predetermined allowable heat generation amount. The control device according to claim 4, wherein the control device is set based on an upper limit shift time determined to be. The torque compensation unit performs control to compensate for the shortage when it is determined that the rotating electrical machine cannot output the necessary input torque during execution of the shift assist control during a power-off downshift. Item 6. The control device according to any one of Items 1 to 5.

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